Contact Formulations for Contact Pairs in Abaqus/Explicit

Modifying the Default Choices for the Contact Pair Weighting

When the kinematic contact method is chosen, you can override the default contact pair weighting only when two separate deformable element-based surfaces are contacting each other, which corresponds to the last situation in each list for kinematic contact given in the previous section.

The following aspects should be considered when deciding whether or not to override the default choice. First, the balanced main-secondary contact algorithm requires more computational time, but it is typically more accurate. Second, when the densities differ by orders of magnitude, the less dense body should be a pure secondary surface. Contact-induced noise can occur if a surface on a much denser body is at all weighted as a secondary surface. Finally, to avoid significant penetration for hard contact, the surface with the finer mesh should not be the main surface in the pure main-secondary contact pair.

When the penalty contact method is chosen, you can choose to specify a pure main-secondary weighting to reduce computational time. When two originally flat surfaces contact one another, a more uniform penetration distance distribution (and consequently pressure distribution) may result with pure main-secondary weighting as compared to balanced main-secondary weighting. This can be particularly evident if the mesh densities of the contacting surfaces differ significantly—with balanced weighting the contact penetrations will be smaller near the nodes of the coarsely meshed surface. However, balanced main-secondary weighting provides better enforcement of contact constraints in most cases.

You define a weighting factor, f, to specify the main-secondary weighting. Set f=1.0 to designate the first surface in the contact pair as the main surface and the second surface as the secondary surface. Set f=0.0 to designate the first surface in the contact pair as the secondary surface and the second surface as the main surface. Specifying any value of f between 0 and 1.0 invokes the balanced main-secondary contact algorithm. When f=0.5, which is the default for balanced main-secondary contact pairs, Abaqus/Explicit weights each set of corrections equally. In contrast, Abaqus/Standard uses a pure main-secondary contact algorithm; the secondary surface must always be given first, as in the f=0.0 case above.

CONTACT PAIR, WEIGHT=f

Interaction module: interaction editor: Weighting factor Specify f

Example

The following input defines finite-sliding contact between the surfaces ASURF and BSURF, shown in Figure 1, with ASURF acting as the secondary surface:

SURFACE,NAME=ASURF
ESETA,
SURFACE,NAME=BSURF
ESETB,
CONTACT PAIR,INTERACTION=PAIR1, WEIGHT=0.0
ASURF, BSURF
SURFACE INTERACTION,NAME=PAIR1

Figure 1. Contacting bodies.

In the example shown in Figure 1 secondary node 101 may come into contact anywhere along the main surface BSURF. While in contact, it is constrained to slide along BSURF, irrespective of the orientation and deformation of this surface. This behavior is possible because Abaqus/Explicit tracks the position of node 101 relative to the main surface BSURF as the bodies deform. Figure 2 shows the possible evolution of the contact between node 101 and its main surface BSURF. Node 101 is in contact with the element face with end nodes 201 and 202 at time $t_1$ . The load transfer at this time occurs between node 101 and nodes 201 and 202 only. Later on, at time $t_2$ , node 101 may find itself in contact with the element face with end nodes 501 and 502. Then the load transfer will occur between node 101 and nodes 501 and 502.

Figure 2. Trajectory of node 101 in finite-sliding contact.

Finite Sliding in a Geometrically Linear Analysis

Finite-sliding simulations usually include nonlinear geometric effects because such simulations generally involve large deformations and large rotations. However, it is also possible to use the finite-sliding formulation in a geometrically linear analysis (see Geometric Nonlinearity). The load transfer paths between the surfaces and the contact direction are updated in finite-sliding, geometrically linear analysis. This capability is useful for analyzing finite sliding between two stiff bodies that do not undergo large rotations.

Anchor Point and Tangent Plane Definition

The anchor point and the tangent plane orientation are chosen before the analysis starts using the initial configuration of the model. The anchor point and the tangent plane orientation remain fixed with respect to the main surface facet for all steps in which the contact pair is active. No contact constraints are enforced for secondary nodes whose nearest point lies on the free perimeter of the main surface in the original configuration and that do not project onto any main surface facet.

Abaqus/Explicit chooses the anchor point as the nearest point on the main surface. The orientation of the tangent plane is calculated by default from the normals at the main surface nodes, or you can specify it directly.

• Main surface normals: The first step in defining the tangent plane orientation is to construct the unit normal vectors at each node of the main surface. Abaqus/Explicit forms these nodal normals by averaging the normals of the element faces making up the main surface; only the element faces in the surface definition will contribute to the nodal normals. The tangent plane orientation is then calculated from the main surface nodal normals and the element shape functions at the anchor point.

  Figure 3 shows the nodal unit normals for a main surface, the anchor point ${\mathbf{X}}_0$ , and the local tangent plane associated with secondary node 103. Abaqus/Explicit uses the closest point on the main surface as the anchor point. $\mathbf{N}\left({\mathbf{X}}_{\mathbf{0}}\right)$ is the contact direction for secondary node 103 and defines the orientation of the local tangent plane. In this example, as in many cases, the local tangent plane is only an approximation of the actual mesh geometry.

• Main surface normals at symmetry planes: Sometimes the main surface normal and the local tangent plane that Abaqus/Explicit calculates are not suitable for the desired analysis. The most common situation where unsuitable surface normals are calculated occurs when a curved main surface ends at a symmetry plane and the boundary conditions have been specified in direct format rather than in symmetry “type” format (XSYMM, YSYMM, or ZSYMM—see Boundary Conditions). In this case the correct normals should be in the symmetry plane; however, because the surface facets that abut the symmetry plane usually form an angle with the plane, the normal will project away from the symmetry plane. The effect of this behavior can be that a secondary node does not project onto any main surface facet (the secondary node is said not to “intersect” the main surface). No contact constraints will be enforced for such secondary nodes. However, if symmetry “type” format boundary conditions are specified, contact constraints will be enforced as described below. The finite-sliding formulations use no special treatment for main surfaces ending at a symmetry plane.

  Figure 4 shows two concentric cylinders that contact each other; the inner cylinder is chosen as the main surface CSURF, and a half-symmetry model is used. Since Abaqus/Explicit calculates the nodal normals from the approximate, finite element model, the nodal normal ${\mathbf{N}}_{\mathbf{1}}$ does not point along the symmetry plane, which means that secondary node 100 has no anchor point within the perimeter of the main surface. Whether or not contact is enforced for node 100 depends on how the symmetry boundary condition is specified. If the individual components are specified rather than a symmetry “type” boundary condition, secondary node 100 will be free to penetrate the main surface. If the symmetry “type” format is used, the main normal at the node on the symmetry plane will be corrected to lie along the symmetry plane and contact will be enforced on the tangent plane as shown in Figure 5. Defining a YSYMM “type” boundary condition at node 1 to specify the symmetry plane will allow secondary node 100 to see the main surface CSURF.

  Figure 4. Main surface normal at node 1 in a small-sliding model of concentric cylinders. With the default ${\mathbf{N}}_{\mathbf{1}}$ secondary node 100 will never contact CSURF.
  
  

  Figure 5. The modified main surface normal at node 1 of CSURF now allows secondary node 100 to contact CSURF.
  
  

• Modifying the local tangent plane orientation: In some cases the contact direction, $\mathbf{N}\left({\mathbf{X}}_{\mathbf{0}}\right)$ , defined from the main surface averaged normals will not define the contact surface accurately. The most common example of this is a circular surface meshed with nonuniform length facets. Figure 6 shows how the averaged main normals will not be oriented correctly in the radial direction.

  Figure 6. Poorly oriented averaged main surface normals for an irregularly meshed circular surface.
  
  

  In this case you should specify the contact direction directly for each secondary node by defining spatially varying initial clearances (see Specifying Initial Clearance Values Precisely). The location of the anchor point is not affected by reorienting the tangent plane using an initial clearance definition.

Local Tangent Plane Rotation

The local tangent plane is always orthogonal to the contact direction. The contact direction is taken as the interpolated normal of the main surface at the anchor point, $\mathbf{N}\left({\mathbf{X}}_{\mathbf{0}}\right)$ , or as the direction specified with a spatially varying clearance definition (see Specifying Initial Clearance Values Precisely). Once the contact direction has been defined, the orientation of the local tangent plane with respect to the main surface facet remains fixed. Because the small-sliding formulation considers nonlinear geometric effects, Abaqus/Explicit continuously updates the orientation of the local tangent plane to account for the rotation of the main surface facet. The position of the anchor point relative to the surrounding nodes on the main surface facet does not change as the main surface deforms.

Load Transfer

In a small-sliding analysis the secondary node will transfer load to the nodes of the main surface facet containing the anchor point, with the magnitude of the load transferred to each node weighted by its proximity to the anchor point. For example, in Figure 3 node 103 transmits load to both nodes 2 and 3 on the main surface. Thus, if node 103 impacts the local tangent plane, a larger share of the force would be transmitted to node 3 because it is closer to the anchor point ${\mathbf{X}}_{\mathbf{0}}$ .

As a secondary node slides along its local tangent plane, Abaqus/Explicit does not update the distribution of load transferred by a given secondary node to its associated main surface nodes; the distribution is based solely on the position of the anchor point. This is unlike the small-sliding formulation in Abaqus/Standard, which does update the load distribution to the main surface nodes as sliding occurs, so that no net moment is associated with the contact forces acting on secondary and main nodes per active contact constraint, regardless of the amount of sliding. Some net moment will be associated with the contact forces after sliding has occurred with the small-sliding formulation in Abaqus/Explicit. This net moment will not be significant if the sliding is truly small compared to element dimensions, but otherwise it can result in non-physical behavior and poor accounting of energy.

Figure 7 shows the potential problem that arises if small sliding is used but the relative tangential motion of the surfaces is not “small.”

Figure 7. Excessive sliding in a small-sliding contact analysis.

It shows the possible evolution of contact between secondary node 101 in Figure 1 and its main surface BSURF. Using the unit normal vectors ${\mathbf{N}}_{201}$ and ${\mathbf{N}}_{202}$ , the anchor point ${\mathbf{X}}_0$ was found for secondary node 101; for the purposes of this example, assume that it lies at the midpoint of the 201–202 face. With this location of ${\mathbf{X}}_0$ the local tangent plane for node 101 is parallel with the 201–202 face. The load transfer always occurs at the original anchor point between nodes 201 and 202, no matter how far node 101 has slid along the local tangent plane. Therefore, if node 101 moves as shown in Figure 7, it will continue to transmit load equally to nodes 201 and 202 when, in fact, it really slid off the mesh forming the main surface BSURF.

What Can Be Considered Small Sliding

A contact pair in a small-sliding contact simulation should not grossly violate any of the assumptions or limitations outlined above. Adhere to the following guidelines:

• Secondary nodes should slide less than an element length from their corresponding anchor point and still be contacting their local tangent plane. If the main surface is highly curved, the secondary nodes should slide only a fraction of an element length.

• The local tangent planes formed by Abaqus/Explicit should be a good approximation of the mesh geometry; if necessary, use an initial clearance definition (Specifying Initial Clearance Values Precisely) to improve the tangent plane orientation.

• The rotation and deformation of the main surface should not cause the local tangent planes to become a poor representation of the main surface during the course of the analysis.

Main Surface Refinement in Small-Sliding Problems

The basic guidelines for pure main-secondary contact given previously in this section should still be followed in a small-sliding simulation. However, in a small-sliding simulation more thought must be given to the degree of refinement for the main surface.

The smoothly varying main surface normal $\mathbf{N}\left(\mathbf{x}\right)$ and the local tangent planes that are formed with it are crucial to the success of a small-sliding analysis. As has been mentioned previously, there are several methods that can be used to modify $\mathbf{N}\left(\mathbf{x}\right)$ ; however, they only control the initial configuration of the local tangent planes. The deformation and rotation of the main surface can reorient the local tangent planes such that they become a poor representation of the main surface. Figure 8 shows an example where distortion of the main surface results in such a situation.

Figure 8. Main surface deformation in a small-sliding contact analysis can cause problems with the local tangent planes.

This problem can be minimized to some extent by using a more refined mesh on the main surface, thus providing more element faces to control the motion of the tangent planes. Excessive mesh refinement should not be necessary since only small sliding should occur.

Global Contact Searches

A global search determines the globally nearest main surface facet for each secondary node in a given contact pair. A bucket sorting algorithm is used to minimize the computational expense of these searches. A two-dimensional example, without consideration of “buckets,” is shown in Figure 9.

Figure 9. Global search in two dimensions.

The global search computes the distance from node 50 to all of the main surface facets in the same bucket as node 50. It determines that the nearest facet on the main surface to node 50 is the facet of element 10. Node 100 is the node on this facet that is nearest to node 50, and it is designated the tracked main surface node. This search is conducted for each secondary node, comparing each node against all of the facets on the main surface that are in the same bucket.

By default, Abaqus/Explicit performs a global search every one hundred increments for two-surface contact pairs. The frequency of the global search can be manually adjusted, as discussed in Contact Controls for Contact Pairs in Abaqus/Explicit. Despite the bucket sorting algorithm, global searches are computationally expensive: performing a global contact search in every increment will more than double the run time of many Abaqus/Explicit contact analyses.

Local Contact Searches

Abaqus/Explicit uses a local contact search to track the motion of the surfaces during most increments of an analysis. In this approach a given secondary node searches only the facets that are attached to the previously tracked main surface node. Abaqus/Explicit determines which adjacent facet is the nearest to the secondary node. It then determines which node on that facet is the closest main surface node to the secondary node and updates the tracked main surface node. If the closest main surface node is not the same as the previously tracked main surface node, Abaqus/Explicit performs another iteration of the local search.

In the example shown in Figure 10, node 50 moves as shown during an increment. In the first iteration of the search Abaqus/Explicit finds that the main surface facet on element 10 is still the closest facet of those attached to node 100 but that node 101 is now the tracked main surface node. Because the previously tracked node was node 100, Abaqus/Explicit performs another iteration. In this second iteration a new element, element 11, is found to be the closest facet and the closest main surface node is 102. Another iteration is performed because the identity of the tracked main surface node changed. In the third iteration the identity of the tracked node does not change, so Abaqus/Explicit designates node 102 as the tracked main surface node for secondary node 50.

A local search is substantially less expensive computationally than a global search. A slightly more expensive local search algorithm can be employed in situations where contact is not being properly enforced; this alternate algorithm is discussed in Contact Controls for Contact Pairs in Abaqus/Explicit.

Figure 10. Local search in two dimensions.

Tracking Approach for Self-Contact Pairs

Abaqus/Explicit uses similar contact searching methods for simulations with self-contact as for two-surface contact; however, more frequent global searches are often necessary for self-contact problems. By default, contact pairs with self-contact use a global contact search every four increments, compared to every 100 increments for two-surface contact pairs; the frequency of the global searches can be manually adjusted (see Contact Controls for Contact Pairs in Abaqus/Explicit). If several facets that are unconnected to each other are found to be near a secondary node during global tracking, global tracking automatically will be performed more frequently than the specified number of increments. Despite this precaution, the self-contact algorithm will be less robust if you specify a search frequency that is significantly lower than the default.